Rotor Analysis -- Big deformation problem

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Discussion Overview

The discussion revolves around the analysis of rotor deformation during modal analysis using Ansys, specifically addressing the unexpected large deformation values observed in the results. Participants explore the implications of mass-normalized values and the significance of excitation conditions in determining vibration amplitudes.

Discussion Character

  • Technical explanation
  • Conceptual clarification
  • Debate/contested

Main Points Raised

  • One participant reports observing a maximum deformation of 100mm in their rotor analysis, questioning whether this is due to mass-normalized values.
  • Another participant clarifies that modal analysis provides eigenvectors where absolute magnitudes are not significant, only relative magnitudes matter.
  • A further contribution suggests that without specifying excitation conditions, it is impossible to determine a "real value" for vibration amplitude, indicating the indeterminate nature of the analysis for an ideal rotor.
  • A detailed example involving a mass-spring system is provided to illustrate the concept of transient and steady-state solutions, emphasizing the need for boundary conditions to define amplitudes.

Areas of Agreement / Disagreement

Participants generally agree on the limitations of modal analysis in providing absolute deformation values without specified excitation conditions. However, the discussion remains unresolved regarding the best approach to obtain meaningful deformation values in the context of rotor analysis.

Contextual Notes

The discussion highlights the dependence on initial or boundary conditions for determining vibration amplitudes and the role of damping in real systems, which are not fully resolved in the current analysis.

Stef
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Hi everyone,
i am currently doing a rotor analysis with "modal analysis" on Ansys and even though my rotor's specs are L=145mm D=10mm and the rotating velocity is 10000rpm i get a deformation of 100mm at most of the modes. I have read that this might be cause of a mass-normalized value but i am not sure if that's the case. Does anyone know why is this happening and if so, can i change it so i can see the real value?
Thanks in advance.
 

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Modal analysis only gives you the eigenvectors. The absolute magnitudes mean nothing at all, only the relative magnitudes are significant. I suspect that this is what you are seeing; I've seen it myself with FEA modal analysis.
 
Yes it looks like it. Maybe I have to use some other way. Thank you anyway.
 
You speak of wanting to see the "real value." The difficulty with that is that there is no "real value" until you specify the excitation. As long as you analyze an ideal, perfectly balanced rotor, there is not way to evaluate the vibration amplitude; it is indeterminate.

Consider a simple example to clarify this situation. Consider a mass M on a spring with constant K, with position described by x. The equation of motion is
M*DDx + K*x = 0
where D = d/dt.
As you know, the solution is x = A*cos(omega_n*t) + B*sin(omega_n*t)
where
omega_n^2 = K/M
But, and this is the point, A and B cannot be determined without initial or boundary conditions. The solution just described is called the transient (homogeneous) solution. You may wonder why it is called the transient solution when it clearly persists forever.

In the discussion above, damping was omitted, but in all real systems, damping is present. The inclusion of positive damping of any type (viscous, V^2, dry friction, hysteretic, etc) will cause this solution to disappear as the time becomes large.

Now, if we put an excitation term on the right side of the equation, the steady state (particular) solution will have a definite amplitude, but the homogeneous solution is still of undefined amplitude. In many cases, we simply say that enough time has elapsed to cause the transient to disappear.
 
That was very helpful thank you very much for your explanation. Have a nice day.
 

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